JP4748601B2 - Hydraulic control device for automatic transmission and hybrid drive device including the same - Google Patents

Abstract

A hydraulic control apparatus for an automatic transmission includes a forward travel engaging element, a reverse travel engaging element, a first signal electromagnetic valve, a first switching valve, and a second switching valve. The hydraulic control apparatus is structured so as to change the output state of the signal pressure of the first signal electromagnetic valve when changing from the reverse travel shift position and/or shift range to the non-travel shift position and/or shift range and when changing from the forward travel shift position and/or shift range to the non-travel shift position and/or shift range, and to enable quick draining of hydraulic pressure of the hydraulic servo of the reverse travel engaging element and hydraulic pressure of the hydraulic servo of the forward travel engaging element.

Description

  The present invention relates to a hydraulic control device for an automatic transmission mounted on, for example, a vehicle and a hybrid drive device including the same, and more particularly, quick drains an engagement pressure supplied to a hydraulic servo of a friction engagement element. It is related with the hydraulic control apparatus of the automatic transmission comprised as mentioned above, and the hybrid drive device provided with the same.

  In general, in a hydraulic control device for an automatic transmission mounted on a vehicle such as an automobile, the shift position is changed from a non-travel shift position (neutral position, parking position) to a travel shift position (drive) by a driver's shift lever operation. When the position or reverse position is changed, the clutch or brake is engaged by supplying an engagement pressure to the hydraulic servo of the clutch or brake to be engaged. When the position is changed, the clutch or brake is released by discharging (draining) the engagement pressure of the hydraulic servo of the clutch or brake to be released.

  In such a hydraulic control device, a valve for selectively guiding or regulating an original pressure such as a line pressure or a range pressure is interposed in an oil passage for supplying an engagement pressure. When draining the engagement pressure, the drain is discharged through such a valve in order to drain the oil passage to which the engagement pressure is supplied. However, especially when the oil temperature is low and the viscosity is high, the distance between the valve and the oil passage in the oil passage as described above becomes a resistance and the drain is delayed, resulting in the release delay of the clutch and brake. In spite of the non-traveling shift position, the traveling torque may be instantaneously transmitted (so-called engagement remaining occurs).

  Since such a phenomenon is not particularly desired to occur in the reverse direction, it has been proposed that the hydraulic servo engagement pressure of the friction engagement element engaged in the reverse shift position can be quickly drained. (See Patent Document 1). This is in an oil passage for supplying engagement pressure to the hydraulic servo, and a switching valve (see reference numeral 61 in FIG. 5) is provided on the hydraulic servo side, and a solenoid valve (see reference numeral S4 in FIG. 5). ) By switching the switching valve according to the signal pressure of (), by connecting the oil path to the hydraulic servo to the drain port, it is possible to perform a quick drain that drains faster than draining through the oil path supplying the engagement pressure It is said.

JP 2001-343067 A

  By the way, the thing of the said patent document 1 enables the quick drain of only the friction engagement element engaged with a reverse shift position, especially an automatic transmission is applied to the vehicle which has a motor, such as a hybrid vehicle, as a drive source. When used, the motor torque output rises faster than the engine torque output, so the forward shift position can be used, for example, to quickly change from the forward shift position to the reverse shift position. There is also a need for a quick drain of a friction engagement element that engages.

  However, for example, when the quick drain switching valve and the solenoid valve as in the above-mentioned Patent Document 1 are arranged as they are with respect to the oil passage on the friction engagement element side that engages the forward shift position, the quick drain is performed. There are two solenoid valves that output signal pressure, which not only hinders cost reduction of the hydraulic control device, but also, for example, the driver quickly moves the shift lever to change from the reverse shift position to the forward shift position, from the forward shift position. If it is repeated as the reverse shift position,..., It is difficult to adjust the control timing of the two solenoid valves, and there is a possibility that a momentary simultaneous engagement occurs and a shift shock occurs.

  Accordingly, the present invention enables quick draining of the hydraulic servo of the forward friction engagement element and the hydraulic servo of the reverse friction engagement element, while being able to reduce costs and to prevent shift shock. It is an object of the present invention to provide a hydraulic control device for an automatic transmission that can be used, and a hybrid drive device including the same.

The present invention according to claim 1 (see, for example, FIGS. 1 to 9) is engaged when the non-travel shift position (P, N) is changed to the forward shift position (D), and the forward shift position (D ) To the non-traveling shift position (P, N), the forward frictional engagement element (C-1) is released, and the non-traveling shift position (P, N) to the reverse shift position (R). A reverse friction engagement element (B-2) that is engaged when the reverse shift position (R) is changed to the non-travel shift position (P, N). In the hydraulic control device (10) of the automatic transmission (3) provided with:
A first signal solenoid valve (SB) capable of outputting a signal pressure (P _SB );
Reverse engagement oil passages (b1, b3, b8, b9, k1, k2, k3, k4) for supplying the engagement pressure (P _B2 ) to the hydraulic servo (33) of the reverse friction engagement element (B-2) , L1, l2, l3, l4), and communicates the reverse engagement oil passage (especially b9 and k1) based on the output state of the signal pressure (P _SB ) of the first signal solenoid valve (SB). A first switching valve that is switched between an engagement position (left half position in FIG. 4) and a discharge position (right half position in FIG. 4) that can be drained faster than draining using the reverse engagement oil passage. 14)
Interposed in forward engagement oil passages (c1, c3, c4, c6) for supplying an engagement pressure (P _C1 ) to the hydraulic servo (31) of the forward frictional engagement element (C-1), Based on the output state of the signal pressure (P _SB ) of the signal solenoid valve (SB), the engagement position (in particular, the left half position in FIG. 4) communicating the forward engagement oil passage (particularly c3 and c4), and the forward engagement A discharge position (right half position in FIG. 4) capable of draining faster than draining using the oil passage, and a second switching valve (15) switched to
When the reverse shift position (R) is changed to the non-travel shift position (P, N) and when the forward shift position (D) is changed to the non-travel shift position (P, N), change the output state of the signal pressure (P _SB) of the first signal solenoid valve (SB), the hydraulic pressure of the servo (33), and the drive friction engagement of the reverse friction engagement element (B-2) It is possible to perform a quick drain of the hydraulic pressure of the hydraulic servo (31) of the joint element (C-1),
The hydraulic control device (10) of the automatic transmission is characterized by the above.

The present invention according to claim 2 (see, for example, FIG. 1 to FIG. 9) is at least when the oil temperature is low, and changes the output state of the signal pressure (P _SB ) of the first signal solenoid valve (SB). Do a quick drain,
The present invention resides in a hydraulic control device (10) for an automatic transmission according to claim 1.

According to the third aspect of the present invention (see, for example, FIG. 4), the first controllable pressure (P _SL1 ) can be supplied to the hydraulic servo (31) of the forward friction engagement element (C- 1). Equipped with a pressure regulating solenoid valve (SL1),
The forward engagement oil passage is configured to apply the control pressure (P _SL1 ) of the first pressure regulating solenoid valve (SL1) to the hydraulic servo (31) of the forward friction engagement element (C-1). P _C1 ) is a control pressure supply oil passage (c1, c3, c4, c6),
The hydraulic control device (10) for an automatic transmission according to claim 1 or 2, characterized in that

The present invention according to claim 4 (see, for example, FIG. 4) outputs a forward range pressure (P _D ) at the forward shift position (D) and shifts to other shift positions (P, R, N). the forward range pressure (P _D) forward range pressure output port (20b, 20c) to drain the Te and, reverse range and outputs the pressure (P _R), and the other shifts during the reverse shift position (R) position with (P, N, D) and the reverse range pressure output port to drain the rear advance range pressure _{(P R)} at (20d), the valve (20) instead range pressure changeover with,
The second switching valve (15) is configured to move the forward engagement oil to the hydraulic servo (31) of the forward friction engagement element (C-1) at the discharge position (right half position in FIG. 4). Connected to the first forward range pressure oil passage (a1, a3, a4) that communicates the passage (c4, c6) and the forward range pressure output port (20b, 20c),
A hydraulic control device (10) for an automatic transmission according to any one of claims 1 to 3, wherein

According to the fifth aspect of the present invention (see, for example, FIG. 4), the first and second switching valves (14, 15) receive the signal pressure (P _SB ) of the first signal solenoid valve (SB). And urged toward the discharge position (right half position in FIG. 4),
The second switching valve (15) is biased toward the engagement position (left half position in FIG. 4) when the non-travel shift position (P, N) is changed to the forward shift position (D). Connected to the second forward range pressure oil passage (a1, a2, a5, a6, a7) for supplying the forward range pressure (P _D ),
The hydraulic control device (10) for an automatic transmission according to claim 4 is characterized in that:

The present invention according to claim 6 (see, for example, FIG. 4) is interposed in the first forward range pressure oil passage (a1, a3, a4), and the second forward range pressure oil passage (a1, a2, a5, a6). , A7) than the forward range pressure (P _D ) supplied to the second switching valve (15) from the first forward range pressure oil passage (a1, a3, a4) to the second switching valve (15). Delay means (42) for delaying the forward range pressure (P _D ) supplied to the
The hydraulic control device (10) for an automatic transmission according to claim 5 is characterized in that:

According to the seventh aspect of the present invention (see, for example, FIG. 4), the second forward range pressure oil passage (a1, a2, a5, a6, a7) is interposed and the forward range pressure (P _D ) is supplied. 3 Forward range pressure oil passages (a1, a3, a5, a8, a9) are connected to the second forward range pressure oil passages (especially a6 and a7) at the non-traveling shift position (P, N). To the communication position (the left half position in FIG. 4), the forward range pressure (a1, a3, a5, a8, a9) from the third forward range pressure oil passage (a1, a3, a5, a8, a9) at the forward shift position (D). P _D ) is input, and the forward range pressure (P _D ) from the third forward range pressure oil passage (a1, a3, a5, a8, a9) after the forward friction engagement element (C-1) is engaged. ) To block the second forward range pressure oil passage (especially a6 and a7). Sectional position including a third switching valve is switched to the (in Fig. 4 right half position) (12),
It exists in the hydraulic control apparatus (10) of the automatic transmission of Claim 5 or 6 characterized by the above-mentioned.

In the present invention according to claim 8 (see, for example, FIG. 4), the reverse engagement oil passage uses the reverse range pressure (P _R ) as the hydraulic servo (33) of the reverse friction engagement element (B-2). The first reverse range pressure oil passage (b1, b3, b8, b9, k1, k2, k3, k4, l1, l2, l3, l4) to be supplied as the engagement pressure (P _B2 ),
The hydraulic control device (10) for an automatic transmission according to any one of claims 5 to 7, characterized in that

According to the ninth aspect of the present invention (see, for example, FIG. 4), the first switching valve (14) is changed when the non-travel shift position (P, N) is changed to the reverse shift position (R). Connected to the second reverse range pressure oil passage (b1, b3, b4, b5, b6) for supplying the reverse range pressure (P _R ) so as to urge toward the engagement position (left half position in FIG. 4). Become
The hydraulic control device (10) for an automatic transmission according to claim 8 is characterized in that:

According to a tenth aspect of the present invention (see, for example, FIG. 4), the second reverse range pressure oil passage (b1, b3, b4, b5, b6) is interposed and the reverse range pressure (P _R ) is supplied. 3 Communication that is connected to the reverse range pressure oil passage (b1, b3, b4, b7) and communicates with the second reverse range pressure oil passage (especially b5 and b6) at the non-travel shift position (P, N). To the position (left half position in FIG. 4), the reverse range pressure (P _R ) from the third reverse range pressure oil passage (b1, b3, b4, b7) is changed during the reverse shift position (R). And when the reverse range pressure oil pressure (P _R ) is urged from the third reverse range pressure oil passage (b1, b3, b4, b7) after the reverse friction engagement element (B-2) is engaged. Blocking position for blocking the second reverse range pressure oil passage (especially b5 and b6) (in FIG. 4) With a third switching valve that is switched to the half position) (12),
The hydraulic control device (10) for an automatic transmission according to claim 9 is characterized in that:

The present invention according to claim 11 (see, for example, FIG. 4), the reverse friction engagement element comprises a reverse brake (B-2),
The automatic transmission (3) includes a reverse clutch (C-3) that is engaged with the reverse brake (B-2) at the reverse shift position (R).
A second signal solenoid valve (SR) that outputs a signal pressure (P _SR ) when the non-travel shift position (P, N) is changed to the reverse shift position (R);
A second pressure regulating solenoid valve (SL4) capable of supplying a regulated pressure (P _SL4 ) to the hydraulic servo (32) of the reverse clutch (C-3),
The third switching valve (12) includes the second pressure regulating solenoid valve (SL4), the hydraulic servo (32) of the reverse clutch (C-3), and the reverse range pressure output of the range pressure switching valve (20). Between the second pressure regulating solenoid valve (SL4) and the reverse clutch (C-3) at the time of the communication position (left half position in FIG. 4). ) And the hydraulic pressure of the reverse range pressure output port (20d) of the range pressure switching valve (20) and the reverse clutch (C-3) at the cutoff position (right half position in FIG. 4). When the signal pressure (P _SR ) of the second signal solenoid valve ( _SR ) is input, the third reverse range pressure oil passage (b1, b3, b4, b7) is communicated with the servo (32). Regardless of the reverse range pressure (P _R ), the communication position (the left half in FIG. 4) When the signal pressure (P _SR ) of the second signal solenoid valve (SR) is not input, the reverse range from the third reverse range pressure oil passage (b1, b3, b4, b7) The reverse range pressure (P _R ) is changed to the reverse position even when the second pressure regulating solenoid valve (SL 4) is faulty by switching to the cutoff position (right half position in FIG. 4) by the pressure (P _R ). Comprising a security valve for supplying to the hydraulic servo (32) of the clutch (C-3),
The hydraulic control device (10) for an automatic transmission according to claim 10 is characterized in that.

According to the twelfth aspect of the present invention (see, for example, FIGS. 1 to 3), the driving force from the internal combustion engine (4) is applied to the first motor (M1) and the driving shaft (2b) by the power distribution mechanism (PR ₀ ). A hybrid drive unit (2) configured to distribute and to apply a drive force of the second motor (M2) to the drive shaft (2b);
The automatic transmission (3) capable of shifting the rotation of the drive shaft (2b) of the hybrid drive unit (2);
A hydraulic control device (10) for an automatic transmission according to any one of claims 1 to 11,
The hybrid drive device (1) is characterized by the above.

  In addition, although the code | symbol in the said parenthesis is for contrast with drawing, this is for convenience for making an understanding of invention easy, and has no influence on the structure of a claim. It is not a thing.

  According to the first aspect of the present invention, when the reverse shift position is changed to the non-travel shift position and when the forward shift position is changed to the non-travel shift position, the signal pressure of the first signal solenoid valve is output. By changing the state, the first switching valve and the second switching valve are switched to the discharge position, and a quick drain of the hydraulic servo pressure of the reverse friction engagement element and the hydraulic servo pressure of the forward friction engagement element is performed. Therefore, while the quick drain can be performed both when the reverse shift position is changed to the non-travel shift position and when the forward shift position is changed to the non-travel shift position, the solenoid valve is the first. Only one signal solenoid valve is sufficient, cost reduction can be achieved, and control of two solenoid valves, for example, is possible. Without simultaneous engagement due to timing misalignment occurs, it is possible to prevent the shift shock.

  According to the second aspect of the present invention, at least at the time of low oil temperature, since the quick drain is performed by changing the output state of the signal pressure of the first signal solenoid valve, the drain is caused by the high viscosity of the oil. Is delayed, and it is possible to prevent the remaining engagement from occurring.

  According to the third aspect of the present invention, the forward engagement oil passage is a control pressure supply oil passage that supplies the control pressure of the first pressure regulating solenoid valve as the engagement pressure to the hydraulic servo of the forward friction engagement element. Therefore, if the hydraulic pressure of the hydraulic servo of the forward friction engagement element is drained by the pressure regulating operation of the first pressure regulating solenoid valve, there is a risk that the drain will be delayed particularly at low oil temperature. Thus, the quick drain can be performed, so that the remaining engagement can be prevented.

  According to the fourth aspect of the present invention, the second switching valve communicates the forward engagement oil path to the hydraulic servo of the forward friction engagement element and the forward range pressure output port at the discharge position. Since it is connected to the forward range pressure oil passage, the hydraulic servo hydraulic quick drain of the forward friction engagement element can be performed together with the forward range pressure drain via the forward range pressure output port of the range pressure switching valve. it can.

  According to the fifth aspect of the present invention, the second switching valve supplies the forward range pressure so as to be biased toward the engagement position when the non-travel shift position is changed to the forward shift position. Since it is connected to the pressure oil passage, for example, when the driver quickly changes from the reverse shift position to the forward shift position, the signal pressure of the first signal solenoid valve is output and the first switching valve is switched to the discharge position. In addition, the second switching valve can be switched to the engagement position by the forward range pressure regardless of the signal pressure of the first signal electromagnetic valve. Thus, while performing quick drain of the hydraulic servo of the hydraulic servo for the reverse friction engagement element, the engagement friction is supplied to the hydraulic servo of the forward friction engagement element to engage the forward friction engagement element. be able to.

  According to the sixth aspect of the present invention, the first forward range pressure oil passage is interposed between the first forward range pressure oil passage and the forward range pressure oil supplied from the second forward range pressure oil passage to the second switching valve. Is provided with a delay means for delaying the forward range pressure supplied from the first forward range pressure oil passage to the hydraulic servo of the forward friction engagement element. The second switching valve can be switched to the engaged position by the forward range pressure from the second forward range pressure oil passage before the operation. Thus, for example, the forward range pressure is not supplied to the hydraulic servo of the forward friction engagement element in a form of flowing back through the first forward range pressure oil passage for performing quick drain, and the original forward engagement oil is used. The engagement pressure can be supplied to the hydraulic servo of the forward friction engagement element via the path, that is, the forward range pressure is suddenly supplied to the hydraulic servo of the forward friction engagement element. It is possible to prevent sudden engagement of the joint elements.

  According to the seventh aspect of the present invention, the second forward range pressure oil passage is interposed in the second forward range pressure oil passage and connected to the third forward range pressure oil passage for supplying the forward range pressure, and the second forward range pressure pressure is set in the non-traveling shift position. The communication position is switched to a communication position that communicates the oil passage, the forward range pressure from the third forward range pressure oil passage is input at the forward shift position, and the third forward range pressure oil is engaged after the forward friction engagement element is engaged. Since it has a third switching valve that is switched to a shut-off position that shuts off the second forward range pressure oil passage by energizing the forward range pressure from the road, when the non-travel shift position is changed to the forward shift position, The forward range pressure is supplied from the second forward range pressure oil passage to the second switching valve, and the second switching valve can be switched to the engagement position regardless of the signal pressure of the first signal electromagnetic valve. Need After the engagement, the second forward range pressure oil passage is shut off, so that when the forward shift position is changed to another shift position, the second switching valve is discharged by the signal pressure of the first signal solenoid valve. And quick drain can be performed.

  According to the eighth aspect of the present invention, the reverse engagement oil passage is a first reverse range pressure oil passage that supplies the reverse range pressure as an engagement pressure to the hydraulic servo of the reverse friction engagement element. Although there is a possibility that the drain will be delayed at the time of the oil temperature, the quick drain can be performed by switching the second switching valve, so that the remaining engagement can be prevented.

  According to the ninth aspect of the present invention, the first switching valve is configured to supply the reverse range pressure so as to bias the first switching valve toward the engagement position when the non-travel shift position is changed to the reverse shift position. Since it is connected to the pressure oil passage, for example, when the driver quickly changes from the forward shift position to the reverse shift position, the signal pressure of the first signal solenoid valve is output and the second switching valve is switched to the discharge position. The first switching valve can be switched to the engaged position by the reverse range pressure regardless of the signal pressure of the first signal solenoid valve. Thus, while performing quick drain of the hydraulic servo of the forward friction engagement element, the engagement friction is supplied to the hydraulic servo of the reverse friction engagement element to engage the reverse friction engagement element. be able to.

  According to the tenth aspect of the present invention, the second reverse range pressure oil passage is interposed in the second reverse range pressure oil passage and is connected to the third reverse range pressure oil passage for supplying the reverse range pressure, and at the non-travel shift position. It is switched to the communication position that communicates the oil passage, the reverse range pressure oil from the third reverse range pressure oil passage is inputted at the reverse shift position, and the third reverse range pressure oil is engaged after the reverse friction engagement element is engaged. Since it has a third switching valve that is switched to a shut-off position that shuts off the second reverse range pressure oil passage by energizing the reverse range pressure from the road, when the non-travel shift position is changed to the reverse shift position, The reverse range pressure is supplied from the second reverse range pressure oil passage to the first switching valve, and the first switching valve can be switched to the engagement position regardless of the signal pressure of the first signal electromagnetic valve. Together After the engagement, the second reverse range pressure oil passage is shut off, so when the reverse shift position is changed to another shift position, the first switching valve is discharged by the signal pressure of the first signal solenoid valve. It can be switched to a position and a quick drain can be performed.

  According to the eleventh aspect of the present invention, the third switching valve is interposed between the second pressure regulating solenoid valve, the hydraulic servo of the reverse clutch, and the reverse range pressure output port of the range pressure change valve, and is connected to the communication position. In this case, the second pressure regulating solenoid valve and the hydraulic servo of the reverse clutch are communicated, and the reverse range pressure output port of the range pressure switching valve and the hydraulic servo of the reverse clutch are communicated at the cutoff position, When the signal pressure of the second signal solenoid valve is input, it is switched to the communication position regardless of the reverse range pressure from the third reverse range pressure oil passage, and the signal pressure of the second signal solenoid valve is not input. The safety valve that is switched to the shut-off position by the reverse range pressure from the third reverse range pressure oil passage and supplies the reverse range pressure to the hydraulic servo of the reverse clutch even when the second pressure regulating solenoid valve fails Other switching It is possible to switch the communication / blocking of the second reverse range pressure oil passage without providing a new valve. In other words, it is possible to reduce the number by sharing the switching valve, and to reduce the size. Cost can be reduced.

  According to the present invention of claim 12, the hydraulic control device for an automatic transmission according to the present invention can be applied to a hybrid drive device. In the hybrid drive device, for example, when the non-travel shift position is switched to the forward shift position or the reverse shift position, the rising of the torque output of the first and second motors is faster than that of the internal combustion engine. If a remaining engagement occurs in the forward friction engagement element or the reverse friction engagement element, a shift shock occurs. However, according to the present invention, the hydraulic servo of the forward friction engagement element and the hydraulic pressure of the reverse friction engagement element are provided. Since a quick drain for the servo is enabled, shift shock can be prevented.

  Embodiments according to the present invention will be described below with reference to FIGS.

  As shown in FIG. 1, a hybrid drive device 1 to which the present invention can be applied roughly includes a hybrid drive unit 2 that can be connected to an internal combustion engine 4, and rotation output from the hybrid drive unit 2, for example, forward four speeds. And an automatic transmission 3 capable of shifting to a first speed and a reverse first speed.

The hybrid drive unit 2 has a so-called two-motor series / parallel system, and can be connected to the internal combustion engine 4 (as the hybrid drive unit 2) an input shaft 2a, a power distribution planetary gear (power distribution mechanism) PR ₀ , A first motor M1 having a stator M1s and a rotor M1r; a second motor M2 having a stator M2s and a rotor M2r; and a drive shaft 2b connected to an input shaft 3a of an automatic transmission 3 to be described later. Configured. In the present embodiment, for convenience of explanation, the drive shaft 2b and the input shaft 3a will be described separately. However, the drive shaft 2b and the input shaft 3a are formed as a single shaft-like member. It consists of

The power splitting planetary gear PR ₀ is the carrier CR0 which rotatably supports the pinions P0, a sun gear S0 which is meshed with the pinion P0, are also configured with a ring gear R0, which is meshed with the pinion P0, The input shaft 2a is connected to the carrier CR0, the rotor M1r of the first motor M1 is connected to the sun gear S0, and the drive shaft 2b is connected to the ring gear R0. The rotor M2r of the second motor M2 is connected to the drive shaft 2b.

  In the hybrid drive unit 2 configured as described above, when driving rotation is input from the internal combustion engine 4 to the input shaft 2a, the driving rotation of the internal combustion engine 4 is transmitted to the carrier CR0. The driving rotation transmitted to the carrier CR0 is distributed to the first motor M1 from the sun gear S0 when the first motor M1 appropriately performs regenerative control according to the throttle opening and the like. The force becomes a reaction force, and the remaining driving force is distributed to the ring gear R0 and output to the driving shaft 2b.

In addition, the driving force (energy) regenerated by the first motor M1 is charged in a battery (not shown) and used as appropriate for the driving force of the second motor M2. That is, the second motor M2 is appropriately impart driving force in accordance with the throttle opening degree to a drive shaft 2b (when engine braking is regenerated as appropriate), were distributed in the power distributing planetary gear PR ₀ from the internal combustion engine 4 The driving force and the driving force of the second motor M2 are merged and output from the driving shaft 2b.

The rotation speed of the drive shaft 2b at this time, depending on the number of revolutions and the first motor M1 of the internal combustion engine 4, a rotation speed based on the gear ratio of the power distributing planetary gear PR _0, the drive shaft 2b Is the input rotation input to the input shaft 3 a of the automatic transmission 3.

  Further, when the internal combustion engine 4 is stopped, the drive shaft 2b is appropriately driven by the second motor M2 in accordance with the throttle opening degree (appropriate regeneration during engine braking), that is, the second motor M2. Only the driving force is input to the input shaft 3 a of the automatic transmission 3. At this time, the first motor M1 is idling, and no rotation is transmitted to the internal combustion engine 4.

Next, the automatic transmission 3 will be described. The automatic transmission 3 includes an automatic transmission mechanism 5 in a case (mission case) 6, and the automatic transmission mechanism 5 includes an input shaft 3 a connected to the drive shaft 2 b of the hybrid drive unit 2, and not shown. Output shaft 3b connected to the drive wheels of the first and third clutches C-1, C-2, C-3, coaxially with the input shaft 3a and the output shaft 3b. the first and second brake B-1, B-2, one-way clutch F-1, the first planetary gear PR _1, is configured to include a second planetary gear PR _2, and the like.

The first planetary gear PR _1, the carrier CR1 rotatably supports the pinions P1, composed of a single pinion planetary gear having a sun gear S1 and ring gear R1 respectively meshed with the pinions P1. Similarly, the second planetary gear PR ₂ also, the carrier CR2 that rotatably supports the pinions P2, composed of a single pinion planetary gear having a sun gear S2 and ring gear R2 respectively meshed with the pinion P2.

The second sun gear S2 of the planetary gear PR ₂ is connected first clutch (drive friction engagement element) C-1, the rotation of the input shaft 3a is input by the engagement of the first clutch C-1 The On the other hand, the first sun gear S1 of the planetary gear PR _1, together with the connected third clutch (reverse clutch) C-3, is connected to the first brake B-1, the third clutch C-1 The rotation of the input shaft 3a is input by the engagement of the first brake B-1, and the rotation is locked to the case 6 by the engagement of the first brake B-1.

The first planetary gear PR ₁ of the carrier CR1, with being rotatably connected to the second ring gear R2 of the planetary gear PR _2, is connected to the second clutch C-2, by the engagement of the second clutch C-2 The rotation of the input shaft 3a is input. The carrier CR1 and the ring gear R2 are restricted from rotating in one direction with respect to the case 6 by the one-way clutch F-1, and the second brake (reverse friction engagement element, reverse brake) B-2. , And the rotation of the case 6 is locked by the engagement of the second brake B-2. Then, the ring gear R1 of the first planetary gear PR _1, together are rotatably connected to the second carrier CR2 of the planetary gear PR _2, and is connected to the output shaft 3b.

  Next, the operation of the automatic transmission 3 will be described with reference to FIGS. 2 and 3 with reference to FIG.

  For example, in the D (drive) range (forward shift position) and in the first forward speed (1st), as shown in FIG. 2, the first clutch C-1 and the one-way clutch F-1 are engaged. Then, as shown in FIGS. 1 and 3, the input rotation of the input shaft 3a (the drive rotation of the drive shaft 2b of the hybrid drive unit 2) is input to the sun gear S2 via the first clutch C-1. Further, the rotation of the ring gear R2 is restricted in one direction, that is, the reverse rotation of the ring gear R2 is prevented and the rotation is fixed. Then, by the input rotation input to the sun gear S2 and the fixed ring gear R2, the carrier CR2 is decelerated and rotated as the first forward speed, and the decelerated rotation of the first forward speed is output from the output shaft 3b.

  During engine braking (coasting), the brake B-2 is locked to fix the ring gear R2, and the forward gear 1 is maintained in a state that prevents forward rotation of the ring gear R2. . In the first forward speed, the one-way clutch F-1 prevents the second carrier CR2 from rotating in the reverse direction and enables the forward rotation, so that, for example, when switching from the non-traveling shift position to the traveling shift position The first forward speed can be smoothly achieved by the automatic engagement of the one-way clutch F-1.

  In the second forward speed (2nd), as shown in FIG. 2, the first clutch C-1 and the first brake B-1 are engaged. Then, as shown in FIGS. 1 and 3, the input rotation of the input shaft 3a is input to the sun gear S2 via the first clutch C-1. Further, the rotation of the sun gear S1 is fixed by the first brake B-1. Then, the carrier CR2 and the ring gear R1 are decelerated and rotated by the input rotation input to the sun gear S2, and the carrier CR1 and the ring gear R2 are also decelerated and rotated by the carrier CR2 and the ring gear R1 based on the decelerated rotation of the ring gear R1 and the fixed sun gear S1. It becomes decelerated rotation that is decelerated more. The carrier CR2 is decelerated and rotated as the second forward speed by the decelerated rotation of the ring gear R2 and the input rotation of the sun gear S2, and the decelerated rotation of the second forward speed is output from the output shaft 3b.

At the third forward speed (3rd), as shown in FIG. 2, the first clutch C-1 and the second clutch C-2 are engaged. Then, as shown in FIGS. 1 and 3, the input rotation of the input shaft 3a is input to the sun gear S2 via the first clutch C-1, and the input rotation is transferred to the carrier via the second clutch C-2. Input to CR1 and ring gear R2. Then, the input rotation input to the sun gear S2 and the ring gear R2, the second planetary gear PR ₂ is directly coupled, the carrier CR2 is directly coupled rotation as the third forward speed, the forward rotation is output shaft of the third forward speed 3b is output.

  At the fourth forward speed (4th), as shown in FIG. 2, the second clutch C-2 and the first brake B-1 are engaged. Then, as shown in FIGS. 1 and 3, the input rotation of the input shaft 3a is input to the carrier CR1 via the second clutch C-2. Further, the rotation of the sun gear S1 is fixed by the first brake B-1. Then, by the input rotation input to the carrier CR1 and the fixed sun gear S1, the ring gear R1 becomes a speed increasing rotation as the fourth forward speed, and the speed increasing rotation of the fourth forward speed is output via the carrier CR2. Output from the shaft 3b.

  In the reverse speed (Rev) (R range, reverse shift position), as shown in FIG. 2, the third clutch C-3 and the second brake B-2 are engaged. Then, as shown in FIGS. 1 and 3, the input rotation of the input shaft 3a is input to the sun gear S1 via the third clutch C-3. Further, the rotation of the carrier CR1 is fixed by the second brake B-2. Then, the ring gear R1 is rotated in reverse by the input rotation input to the sun gear S1 and the fixed carrier CR1, and the reverse rotation as the reverse gear is output from the output shaft 3b via the carrier CR2.

In the P (parking) range and the N (neutral) range (non-traveling shift position), the first clutch C-1, the second clutch C-2, and the third clutch C-3 are released. Therefore, between the input shaft 3a and the first planetary gear PR ₁ and the second planetary gear PR ₂ is disconnected, the power transmission between the input shaft 3a and output shaft 3b are disconnected.

  The automatic transmission 3 of the hybrid drive device 1 configured as described above includes the first to third clutches C-1, C-2, C-3 and the first to second brakes B-1, B-. Shift control is performed by engaging / disengaging 2 with hydraulic control measures. Hereinafter, the hydraulic control device 10 of the automatic transmission 3 will be described with reference to FIG.

  FIG. 4 shows a main part of the present invention in the hydraulic control device 10, and the actual hydraulic control device 10 is provided with many other valves, oil passages, and the like. In particular, the hydraulic control apparatus 10 according to the present invention includes two linear solenoids that supply control pressures directly to the hydraulic servo of the second clutch C-2 and the hydraulic servo of the first brake B-1, which are not shown. Valves (SL2, SL3, not shown) are provided, and the engagement / disengagement control of the second clutch C-2 and the first brake B-1 is performed by these linear solenoid valves. Are the first clutch C-1, the third clutch C-3, the second brake B-2, and the linear solenoid valves (first pressure regulating solenoid valve, second pressure regulating solenoid valve) SL1, SL4 according to the present invention. We will focus on the parts related to.

In addition, the hydraulic control device 10 includes, for example, an electric oil pump that is driven when the ignition is turned on and a mechanical oil pump that is driven in conjunction with the internal combustion engine 4 (not shown). the hydraulic pressure generated from is pressure regulated to a line pressure P _L corresponding to the throttle opening by the primary regulator valve (not shown). Note that the oil pump may include only an electric oil pump.

As shown in FIG. 4, the manual valve (range pressure switching valve) 20 has a spool 20p. The spool 20p is disposed in a driver's seat (not shown), and is used to select a shift range. It is driven to move in the left-right direction in the figure in conjunction with the lever mechanically or electrically. The manual valve 20 has an input port 20a of the line pressure P _L is input, the input port 20a, particularly when the P range and the N range based on the shift lever operation, which will be described later by the spool 20p The output ports 20b, 20c, and 20d are blocked.

The manual valve 20 has output ports (forward range pressure output ports) 20b and 20c communicating with the input port 20a when the spool 20p is set to the D range position based on the shift lever operation. the time of outputs output port 20b, and the line pressure _{P L} from 20c to the oil passage a1~a10 as the forward range pressure _{P D.} When the shift lever is operated to change to a range other than the D range, that is, when the spool 20p is set to the P range, R range, or N range, the output ports 20b and 20c are connected to the drain port EX. communicating the forward range pressure _{P D} in the oil passage a1~a10 is drained (discharged) via the check ball valve 26.

Further, the manual valve 20 has an output port (reverse range pressure output port) 20d communicating with the input port 20a when the spool 20p is set to the R range position based on the shift lever operation. during range, it outputs the line pressure _{P L} from the output port 20d to the oil passage b1~b9 as reverse range pressure _{P R.} Similarly, when the shift lever is operated to change to a range other than the R range, that is, when the spool 20p is set to the P range, N range, or D range, the output port 20d is connected to the drain port EX. It communicates with, the reverse range pressure _{P R} in the oil passage b1~b9 is drained (discharged) via the check ball valve 25.

  Here, the configuration of the check ball valve will be described with reference to FIG. As shown in FIG. 5 (b), the check ball valve 25 is disposed on the upper side of the vehicle in a normal state with respect to the valve body 50 in which the oil passage constituting the hydraulic control device 10 is formed. . The valve body 50 and the check ball valve 25 are on the lower side of the case 6 that houses the automatic transmission mechanism 5, and a lubricating oil that lubricates the automatic transmission mechanism 5 is formed in a hole formed below the case 6. When the oil flows down, the oil is received and collected in an oil pan that is collected.

  The valve body 50 has a body body 50a in which an oil passage is three-dimensionally formed in a groove shape, and is configured such that the upper side is closed by an upper plate 50g. The body body 50a has a valve hole 50c in which the spool 20p of the manual valve 20 is disposed, and the drain port EX of the manual valve 20 communicates with an oil passage 50b formed in the body body 50a. Has been.

  On the other hand, the check ball valve 25 has a ball valve body 25a, an oil hole 25b drilled in the ball valve body 25a, and a ball having a diameter larger than that of the oil hole 25b and closing the oil hole 25b by its own weight. 25c and a cover 25d covering the ball 25c. The ball valve main body 25a is fixed to the upper plate 50b, and an oil hole is formed in the upper plate 50b so that the oil passage 50b and the oil hole 25b communicate with each other.

  By the way, as described above, the check ball valve 25 and the valve body 50 are disposed on the lower side of the case 6 at positions where the lubricating oil lubricated in the automatic transmission mechanism 5 flows down from above. There is a possibility that iron powder or the like generated in the automatic transmission mechanism 5 is mixed in the lubricating oil, and the iron powder may enter the check ball valve 25. Needless to say, if the check ball valve is arranged downward, it cannot be blocked by the ball, and the oil may flow down and cause air contamination.

  Therefore, for example, when the ball valve main body 125a is covered by the cover 125d when the check ball valve 125 and the valve body 150 shown in FIG. 5A are configured, iron powder may enter the portion of the ball 125c. Yes, when the ball 125c is lifted upward by the hydraulic pressure discharged from the drain port EX of the manual valve 20, the iron powder enters the oil passage 150b of the body main body 150a through the oil hole 125b and the oil hole of the upper plate 150g, Since the valve hole 150c of the manual valve 20 is formed below the oil passage 150b, iron powder may be caught between the spool 20p and the valve hole 150c to cause a valve stick.

  Therefore, in the valve body 50 in the present embodiment, as shown in FIG. 5B, a partition 50d is provided in the oil passage 50b of the body main body 50, and the oil passage 50b is connected to the first chamber 50e. It is configured separately from the second chamber 50f. That is, a first chamber 50e is formed below the oil hole 25b of the check ball valve 25 so as to be an oil reservoir by the partition portion 50d, and iron powder has entered through the check ball valve 25 by any chance. However, it is configured such that it is deposited in the first chamber 50e and is difficult to enter the second chamber 50f. This prevents the valve stick as described above from occurring.

  In the above description, the check ball valve 25 is described as an example, but the other check ball valves 26, 27, 28, etc. in the hydraulic control apparatus 10 are all configured in the same manner, and in particular the check ball valve. Even if the valve disposed in the vicinity of the valve is a valve that generates magnetic force, such as a linear solenoid valve, valve stick prevention is similarly achieved.

On the other hand, as shown in FIG. 4, in the hydraulic control apparatus 10, the oil passage a1 connected to the output ports 20b and 20c of the manual valve 20 is connected to the input port SL1a of the linear solenoid valve SL1 via the oil passage a2. are, in other words the linear solenoid valve SL1 is forward range pressure P _D is input as a source pressure. The linear solenoid valve SL1 includes a spool (not shown), the input port SL1a, an output port SL1b connected to the oil passage c1, and a feedback oil chamber for inputting feedback pressure from the oil passage c1 through the oil passage c2. SL1c and a drain port SL1d connected to an oil passage c7 communicating with the check ball 27 are configured.

The linear solenoid valve SL1 is, for example, a normal / open type, and when energized, the spool cuts off the input port SL1a and the output port SL1b and communicates between the output port SL1b and the drain port SL1d. The spool is moved and driven in response to the weakening of the energized current, and the output port SL1b and the drain port SL1d are gradually cut off, and the input port SL1a and the output port SL1b they gradually communication is between, whereby, while being feedback controlled by a feedback pressure to be input to the feedback oil chamber SL1c, the forward range pressure P _D is the pressure regulating as the control pressure P _SL1 from the output port SL1b input port SL1a Is output.

The linear solenoid valve SL4 is the line pressure _{P L} is input as an original pressure to the input port SL4a. The linear solenoid valve SL4 includes a spool (not shown), the input port SL4a, an output port SL4b connected to the oil passage d1, and a feedback oil chamber for inputting feedback pressure from the oil passage d1 through the oil passage d2. SL4c and a drain port SL4d connected to an oil passage d4 communicating with the check ball valve 28 are configured.

The linear solenoid valve SL4 is of, for example, a normal / close type, and the input port SL4a and the output port SL4b are blocked by the spool when not energized, and the output port SL4b and the drain port SL4d communicate with each other. Then, the spool is moved and driven according to the intensity of the energized current, and the output port SL4b and the drain port SL4d are gradually cut off, and the input port SL4a and the output port SL4b are gradually cut off. will be communicated to, thereby, being feedback controlled by a feedback pressure to be input to the feedback oil chamber SL4c, the line pressure P _L input ports SL4a is pressure regulating output as the control pressure P _SL4 from the output port SL4b.

On the other hand, the solenoid valve (second signal solenoid valve) SR has an input port SRa for inputting a modulator pressure P _MOD from a modulator valve (not shown) and an output port SRb connected to the oil passages h1, h2, and h3. It is configured. Incidentally, a modulator valve inputs the line pressure P _L, when the line pressure P _L to be increased based on the throttle opening degree is equal to or higher than a predetermined pressure, on the urging force of the spring that urges the spool and the feedback pressure This is a valve that outputs as a constant pressure modulator pressure P _MOD .

The solenoid valve SR is, for example, a three-way normal / closed type, and the input port SRa and the output port SRb are disconnected when not energized, and the input port SRa and the output port SRb are energized when energized. between is communicated to output from the output port SRb the signal pressure _{P SR} to the oil passage h1, h2, h3.

Similarly, the solenoid valve (first signal solenoid valve) SB also has an input port SBa for inputting a modulator pressure P _MOD from a modulator valve (not shown), and an output port SBb connected to the oil passages i1, i2, i3. For example, a three-way normal / closed type, the input port SBa and the output port SBb are cut off when not energized, and the input port when energized. between SBa and output ports SBb communicates is outputted from the output port SBb the signal pressure P _SB in the oil path i1, i2, i3.

The C3B2 relay valve 11 includes a spool 11p, a spring 11s that urges the spool 11p in one direction (upper side in FIG. 4), a hydraulic oil chamber 11a to which the modulator pressure _PMOD is input, and the manual valve 20 output port 20b, the forward range pressure from 20c _{P D} is an oil passage a1, a3, a5, a8, a hydraulic oil chamber 11b which is input via the a10, reverse range pressure from the output port 20d of the manual valve 20 an input port 11c of P _R is input via the oil passage b1, b2, an input port 11d to the control pressure _{P SL4} from the output port SL4b of the linear solenoid valve SL4 through the oil passage d1, d2 are input , An output port 11e connected to the oil passage e1, an output port 11f connected to the oil passage f1, and a solenoid via the oil passage h2. Is configured to include a hydraulic oil chamber 11g the signal pressure P _SR of maytansinoid valve SR is input.

The C3B2 relay valve 11, for example, when the ignition is is ON by the line pressure _{P L} occurs, the modulator pressure _{P MOD} in the hydraulic oil chamber 11a is input, by overcoming the urging force of the spring 11s, the spool 11p is 4 This is the position indicated by the middle right half (hereinafter referred to as “right half position”). When the right-half position, the input port 11d and the output port 11e are communicated, i.e. the control pressure P _SL4 linear solenoid valve SL4 supplied to the oil passage d3 can be supplied to the oil path e1.

Furthermore, the C3B2 relay valve 11, the when the right half position state signal pressure _{P SR} to the hydraulic oil chamber 11g from is input, the signal pressure _{P SR} of the biasing force and hydraulic oil chamber 11g of the spring 11s is hydraulic oil chamber Overcoming the modulator pressure P _{MOD of} 11a, the spool 11p is in the position indicated by the left half in FIG. 4 (hereinafter referred to as “left half position”). When the left-half position, communicates the output port 11e and the input port 11c, also, the input port 11d and the output port 11f are communicated, i.e. reverse range pressure from the manual valve 15 P _R is the oil path e1 together it can be supplied to the control pressure P _SL4 linear solenoid valve SL4 supplied to the oil passage d3 can be supplied to the oil passage f1.

Furthermore, the C3B2 relay valve 11, the forward range pressure P _D to the hydraulic oil chamber 11b from the state of the left half position is input, regardless of the input state of the signal pressure P _SR of the hydraulic oil chamber 11g, hydraulic oil chamber and the modulator pressure _{P MOD} and the forward range pressure _{P D} of the hydraulic oil chamber 11b of 11a is overcoming the biasing force of the spring 11s (and the hydraulic oil chamber 11g of the signal pressure _{P SR} (when the signal pressure _{P SR} is input)) This is the right half position described above.

The C3 relay valve (third switching valve, security valve) 12 includes a spool 12p, a spring 12s that urges the spool 12p in one direction (upper side in FIG. 4), an output port 20b of the manual valve 20, forward range pressure from 20c _{P D} is an oil passage a1, a3, a5, a8, a hydraulic oil chamber 12a that is input via the a9, reverse range pressure _{P R} is the oil path from the output port 20d of the manual valve 20 b1, b3, b4, b7 and hydraulic oil chamber 12b which is input via the an input port 12c of the control pressure _{P SL4} from the linear solenoid valve SL4 via the oil passage f1 is input, connected to an oil passage g1 an output port 12d that is, specifically the reverse range pressure _{P R} is of the input of the oil passage e1, e2, and the B2 relay valve 14 via the oil passage k4, k5 to be described later An input port 12e to an input port 12f of the forward range pressure _{P D} from the output port 20b, 20c of the manual valve 20 is input via the oil passage a1, a3, a5, a6, are connected to the oil passage a7 and an output port 12g, the reverse range pressure _{P R} is an input port 12h, which is input via the oil paths b1, b3, b4, b5, an output connected to an oil passage b6 from the output port 20d of the manual valve 20 It has a port 12i and a hydraulic oil chamber 12j into which the signal pressure PSR of the solenoid valve _SR is input via the oil passage h3.

The C3 relay valve 12, the forward range pressure _{P D} to the hydraulic oil chamber 12a is, or to the hydraulic oil chamber 12b is reverse range pressure _{P R} is input, by overcoming the urging force of the spring 12s, the spool 12p Is in the right half position. In the right half position, the input port 12c and the output port 12d are blocked, and the input port 12e and the output port 12d are communicated, that is, supplied to the oil passage k5 via the B2 relay valve 14 described later. reverse range pressure P _R can be supplied to the oil path g1 that. In the right half position, the input port 12f and the output port 12g are blocked, the output port 12g and the drain port EX are communicated, the input port 12h and the output port 12i are blocked, and passed output port 12i and the drain port EX are communicated, i.e. the forward range pressure P _D of the oil passage a7 is drained, and the reverse range pressure P _R of the oil passage b6 is drained.

Further, the C3 relay valve 12, when the signal pressure _{P SR} is input to the hydraulic oil chamber 12j, the reverse range pressure input condition or the hydraulic oil chamber 12b of the forward range pressure _{P D} of the hydraulic oil chamber 12a P regardless of the input state of the _R, the left-half position by the signal pressure P _SR of the biasing force and hydraulic oil chamber 12j of the spring 12s is overcome. When the left half position is reached, the input port 12e and the output port 12d are shut off, and the input port 12c and the output port 12d are communicated, that is, the control pressure P of the linear solenoid valve SL4 via the oil passage f1. _SL4 can be supplied to the oil passage g1. Further, when the left-half position, the input port 12f and the threaded output port 12g are communicated, also passed through the output port 12i are communicated and the input port 12h, i.e. the forward range pressure P _D is output to the oil passage a7 and the reverse range pressure _{P R} is output to the oil passage b6.

  The oil passage g1 connected to the output port 12d of the C3 relay valve 12 communicates with the oil passages g2 and g3, and is connected to the damper 23 through the oil passage g3. 3 hydraulic servo 32. Further, a check ball 43 is interposed between the oil passage g1 and the oil passage g2. The check ball 43 includes an orifice 43a and an orifice 43b that are interposed in each of two branched oil passages, and a ball 43c that can come into contact with and separate from the orifice 43a. Compared to the supply speed of the third clutch C-3 to the hydraulic servo 32 to the path g3, the drain speed from the oil path g3 to the oil path g1 is increased.

The damper 23 includes an oil chamber 23a, a spring 23s, and a piston 23p biased in the direction toward the oil chamber 23a by the spring 23s. , That is, the pulsation of the engagement pressure P _C3 (that is, the control pressure P _SL4 or the reverse range pressure P _R ) supplied to the hydraulic servo 32 of the third clutch C-3 is reduced.

On the other hand, the B2 cut-off valve 13 includes a spool 13p, a spring 13s that urges the spool 13p in one direction (upward in FIG. 4), and a hydraulic servo of the first brake B-1 (not shown). a hydraulic oil chamber 13a of application pressure _{P B1} is input, likewise a hydraulic oil chamber 13b of the engagement pressure _{P C2} is input from the hydraulic servo of the second clutch C2, not shown, connected to the oil passage e1 Input port 13c and an output port 13d connected to the oil passage e2.

When the engagement pressure P _B1 is input to the hydraulic oil chamber 13a or the engagement pressure P _C2 is input to the hydraulic oil chamber 13b, the B2 cut-off valve 13 overcomes the urging force of the spring 13s and moves to the right half. Position. When the right-half position, the input port 13c and the output port 13d is cut off, i.e. the control pressure P _SL4 or reverse range pressure P _R of the linear solenoid valve SL4 supplied from the oil path e1 is blocked.

Further, the B2 cut-off valve 13, if it is a state where the engagement pressure _{P B1} and the engagement pressure _{P C2} to the hydraulic oil chamber 13a and the hydraulic oil chamber 13b is not input both the left due to the urging force of the spring 13s Half position. When the left-half position, the input port 13c and the threaded output port 13d are communicated, i.e. the control pressure P _SL4 or reverse range pressure P _R of the linear solenoid valve SL4 supplied via the oil path e1 is the oil passage e2 Supplied.

The B2 relay valve (first switching valve) 14 includes a spool 14p, a spring 14s that urges the spool 14p in one direction (upper side in FIG. 4), and a signal pressure P from the output port SBb of the solenoid valve SB. Hydraulic oil chamber 14a to which _SB is input, output port 14b connected to oil passage j1, input port 14c connected to oil passage e2, and reverse range via oil passages b1, b3, b8, b9 an input port 14d to pressure P _R is input, an output port 14e that is connected to the oil passage k1, and is configured to have a hydraulic oil chamber 14f that is connected to the oil path b6, the.

A check ball 46 is interposed between the oil passage b8 and the oil passage b9. The check ball 46 includes an orifice 46a and an orifice 46b interposed in each of the two branched oil passages, and a ball 46c that can come into contact with and separate from the orifice 46a. compared to the feed rate of the reverse range pressure P _R to the road b9, the drain rate from the oil passage b9 to the oil passage b8 is configured to be lower.

The B2 relay valve 14, when there with no signal pressure P _SB to the hydraulic oil chamber 14a is input, the left-half position due to the urging force of the spring 14s. When the left half position is reached, the input port 14c is shut off, the output port 14b and the drain port EX are communicated, and the input port 14d and the output port 14e are communicated, and the reverse range pressure P from the oil passage b9. _R is supplied to the oil passage k1.

Furthermore, the B2 relay valve 14, when the signal pressure P _SB to the hydraulic oil chamber 14a is input, the right-half position by overcoming the urging force of the spring 14s. When in the right half position, the input port 14c and the output port 14b are communicated, and the output port 14e and the drain port EX are communicated, that is, the control pressure P of the linear solenoid valve SL4 supplied from the oil passage e2. _SL4 or reverse range pressure P _R together is in a state capable of supplying to the oil passage j1, the hydraulic oil pressure in the oil passage k1 is drained.

Furthermore, the B2 relay valve 14, regardless of the input state of the signal pressure P _SB of the hydraulic oil chamber 14a, when the reverse range pressure P _R is supplied to the hydraulic oil chamber 14f, is switched to the left half position described above .

  The oil passage j1 is connected to the input port 21b of the check valve 21, and the oil passage k1 is connected to the input port 21a of the check valve 21 via the oil passage k4. The check valve 21 has the input port 21a, the input port 21b, and an output port 21c connected to the oil passage l1, so that the oil pressure in the oil passage j1 and the oil pressure in the oil passage k4 are The higher oil pressure communicates with the oil passage l1, and the lower oil passage and l1 are blocked. The oil passage k4 is connected to the oil passage k5, and the oil passage k5 is connected to the input port 12e of the C3 relay valve 12.

  A check ball 45 is interposed between the oil passage k2 and the oil passage k3. The check ball 45 is configured to include an orifice 45a and a ball 45b that can be brought into contact with and separated from the orifice 46a. The check ball 45 permits oil pressure to be supplied from the oil path k2 to the oil path k3. The drain to the path k2 is configured to be shut off, that is, the backflow of hydraulic pressure from the oil path k3 to the oil path k2 is prevented.

  The hydraulic servo 33 of the second brake B-2 is a so-called double piston type hydraulic servo, and has a B-2 outer oil chamber 33a and a B-2 inner oil chamber 33b. The B-2 outer oil chamber 33a is connected to the oil passage k3, and the B-2 inner oil chamber 33b is connected to the oil passage l2 and connected to the oil passage l1. The oil path k3 and the oil path l2 are connected by an oil path l33, a check ball 44, and an oil path l4. The check ball 44 includes an orifice 44a and an orifice 44b interposed in each of the two branched oil passages, and a ball 44c that can come into contact with and separate from the orifice 44a. The drain speed from the oil passage 14 to the oil passage 13 is higher than the supply speed of the hydraulic pressure to the passage 14. As a result, the oil pressure in the oil passage l2 is not always lower than the oil pressure in the oil passage k3, that is, the oil pressure in the B-2 outer oil chamber 33a is higher than the oil pressure in the B-2 inner oil chamber 33b. This prevents the partition wall (not shown) that separates between the B-2 outer oil chamber 33a and the B-2 inner oil chamber 33b from moving.

On the other hand, the C1 relay valve (second switching valve) 15 includes a spool 15p, a spring 15s that urges the spool 15p in one direction (upper side in FIG. 4), and a signal pressure P _SB from the solenoid valve SB. a hydraulic oil chamber 15a that is input via the oil paths i1, i3, an input port 15b of the control pressure _{P SL1} from the linear solenoid valve SL1 via the oil passage c3 is inputted, it is connected to the oil passage c4 An output port 15c, a connection port 15d connected to the output ports 20b and 20c of the manual valve 20 via oil passages a1, a3 and a4, and oil passages a1, a3, a5 and a6 via the oil passage a7 forward range pressure P _D from is a hydraulic oil chamber 15e to be input.

The C1 relay valve 15, if it is a state where the signal pressure P _SB to the hydraulic oil chamber 12a is not input, the left-half position by the biasing force of the spring 15s. When the left-half position, the input port 15b and the threaded output port 15c are communicated, i.e. the control pressure P _SL4 linear solenoid valve SL4 can be supplied to the oil passage c4 via the oil passage c3.

Further, the C1 relay valve 15, when the signal pressure P _SB is input via the oil passage i3 to the hydraulic oil chamber 15a, the right-half position by overcoming the urging force of the spring 15s. In the right half position, the input port 15c and the connection port 15d are communicated, that is, the oil passage c4 and the output ports 20b and 20c of the manual valve 20 are communicated.

Furthermore, the C1 relay valve 15, regardless of the input state of the signal pressure P _SB of the hydraulic oil chamber 15a, the forward range pressure P _R is supplied to the hydraulic oil chamber 15e, is switched to the left half position described above .

  The oil passage c4 connected to the connection port 15d of the C1 relay valve 15 communicates with the oil passages c5 and c6, is connected to the damper 22 via the oil passage c5, and is connected to the first clutch C- 1 hydraulic servo 31 is connected. A check ball 41 is interposed between the oil passage c4 and the oil passage c6. The check ball 41 includes an orifice 41a and an orifice 41b interposed in each of the two branched oil passages, and a ball 41c that can freely contact and separate from the orifice 41a. The drain speed from the oil path c6 to the oil path c4 is higher than the supply speed to the hydraulic servo 31 of the first clutch C-1 to the path c6.

The damper 22 includes an oil chamber 22a, a spring 22s, and a piston 22p biased in the direction toward the oil chamber 22a by the spring 22s. , That is, the pulsation of the engagement pressure P _C1 (that is, the control pressure P _SL1 ) supplied to the hydraulic servo 31 of the first clutch C- 1 is reduced.

  Next, the operation of the hydraulic control apparatus 10 based on the configuration described above will be described.

  The driver selects and operates the D position (forward shift position) with the shift lever, and the spool 20p of the manual valve 20 is in the D range position. In the state where the stage (1ST) is determined, the solenoid valve SR and the solenoid valve SB are turned off by an electronic command from the control unit.

Then, C3 relay valve 12, the output port 20b of the manual valve 20 to the hydraulic oil chamber 12a, the forward range pressure _{P D} is output from 20c is input via the oil paths a1, a3, a5, a9, right half position It becomes. Thereby, the output port 20b of the manual valve 20, 20c oil passages a1, a3, a5, a6 forward range pressure _{P D} is input via the is cut off from the forward range pressure _{P D} to the oil passage a7 output Not.

Therefore, the C1 relay valve 15, the signal pressure _{P SB} to the hydraulic oil chamber 15a is also forward range pressure _{P D} is not supplied to the hydraulic oil chamber 15e, by the urging force of the spring 15s, the left-half position. Thereby, the input port 15b and the output port 15c are communicated, and the oil passages c1, c3, c4, c5, and c6 (forward engagement oil passage, control pressure supply oil passage) are communicated. Then, the input port SL1a of the linear solenoid valve SL1 is supplied with the forward range pressure _{P D,} from the output port SL1b as the linear solenoid valve SL1 is the forward range pressure _{P D} dimming pressure control to control pressure _{P SL1} by outputting, while the control pressure _{P SL1} is pulsation reduced by the damper 22, is supplied to the hydraulic servo 31 of the first clutch C1 as the engagement pressure _{P C1,} first clutch C1 is engaged Is done. At the first forward speed, the one-way clutch F-1 is engaged together with the first clutch C-1 (see FIGS. 1 to 3), and the first forward speed is achieved.

Further, C3B2 relay valve 11, the modulator pressure _{P MOD} is input to the hydraulic oil chamber 11a, the oil passage a1, a3, a5, a8, the forward range pressure _{P D} via the a10 is input to the hydraulic oil chamber 11b, actuation since the oil chamber 11f is signal pressure P _SR not input, the right-half position. In the first forward speed, the second clutch C-2 and the first brake B-1 are not engaged, that is, the engagement pressure P _B1 and the engagement pressure P _C2 are not generated. The off valve 13 is in the left half position. Further, the B2 relay valve 14 is in the left half position because the signal pressure _PSB is not input to the hydraulic oil chamber 14a. Further, C3 relay valve 12, the forward range pressure _{P D} to the hydraulic oil chamber 12a is input, the signal pressure _{P SR} to the hydraulic oil chamber 12f is not input, the right-half position.

From this state, when it is determined by the control unit (not shown) that the engine is in the first forward speed, the solenoid valve SB is turned on and the B2 relay valve 14 is switched to the right half position. solenoid valve SL4 is controlled drive, the control pressure _{P SL4} from the output port SL4b is outputted to the oil passage d1, d3, through the C3B2 oil passage e1, e2, j1, l1, l2 from the output port 11e of the relay valve 11 control pressure _{P SL4} is supplied to the B2 inner oil chamber 33b as the engagement pressure _{P B2} of the second brake B2, the second brake B2 is engaged. Since the oil path k2 and the oil path k3 are blocked by the check ball 45, the control pressure _PSL4 is gradually supplied to the B-2 outer oil chamber 33a through the oil paths l3 and l4.

When the controller determines that the first forward speed is positively driven (when the engine is not braked), the linear solenoid valve SL4 is controlled and the oil passages l4, l3, l2, l1, j1, e2, and so on. The engagement pressure P _{B2 of} the second brake B-2 is drained from the drain port SL4d via the check ball valve 28 via e1, d3, and d1, and the second brake B-2 is released. Thereafter, when the second brake B-2 is completely released, the solenoid valve SB is turned OFF, and the B2 relay valve 14 is switched to the left half position by the urging force of the spring 14s.

In the second forward speed to the fourth forward speed, at least one of the first brake B-1 and the second clutch C-2 is engaged, so the B2 cutoff valve 13 is in the right half position. Since the oil path d1 and the oil path e1 are blocked and the oil path e2 communicates with the drain port EX, the control pressure PSL4 from the linear solenoid valve _SL4 is set to B-2 outer oil chambers 32a and B-2. The oil pressure is not supplied to the inner oil chamber 32b and is drained. For example, even if the first brake B-1 and the second clutch C-2 are engaged at the time of engine braking at the first forward speed due to some failure, the second brake B-2 is Simultaneous engagement of the two clutches C-2 is prevented, that is, the stall state of the automatic transmission 3 is prevented.

Further, for example, in this first forward speed, when the linear solenoid valve SL4 fails and the control pressure _PSL4 is not output, the second brake B-2 cannot be engaged, but as described above. In addition, since the one-way clutch F-1 ensures the positive drive state, the limp home function is sufficient.

  On the other hand, the driver selects and operates the R position (reverse shift position) with the shift lever, and the spool 20p of the manual valve 20 is in the R range position. When the stage (REV) is determined, the solenoid valve SR is turned on and the solenoid valve SB is turned off by an electronic command from the control unit.

Then, C3B2 relay valve 11 is the modulator pressure _{P MOD} to the hydraulic oil chamber 11a is input, the forward range pressure _{P D} is not supplied to the hydraulic oil chamber 11b, the hydraulic oil chamber 11g to the signal pressure _{P SR} is input Therefore, the left half position is obtained. Further, C3 relay valve 12 is reverse range pressure _{P R} to the hydraulic oil chamber 12b is input, the signal pressure _{P SR} is input to the hydraulic oil chamber 12f, the left-half position. Even in the reverse speed, the second clutch C-2 and the first brake B-1 are not engaged, that is, the engagement pressure P _B1 and the engagement pressure P _C2 are not generated. 13 is the left half position. Furthermore, B2 relay valve 14, the signal pressure _{P SB} is not input to the hydraulic oil chamber 14a, since the reverse range pressure _{P R} to the hydraulic oil chamber 14f is not input by the biasing force of the spring 14s, the right-half position.

From this state, the linear solenoid valve SL4 is controlled driven by the control unit, when the control pressure _{P SL4} is output from the output port SL4b, pulsation by the oil passage d1, d3, f1, g1, g2, g3 damper 23 via the There the control pressure _{P SL4} is supplied to the hydraulic servo 32 as an engagement pressure _{P C3} of the third clutch C3 being reduced.

On the other hand, the reverse range pressure _{P R} from the manual valve 20 is, the oil passage b1, b3, b8, b9, B2 is outputted from the output port 14e via the input port 14d of the relay valve 14, the reverse range pressure P to the oil passage k1 _R is supplied. Therefore, the reverse range pressure _{P R} is, the oil passage k1, k4, check valve 21, the oil passage l1, through l2 B-2 inner oil chamber 33b, also, the oil passage k2, the check ball 45, the oil passage k3 To the B-2 outer oil chamber 33a, and the second brake B-2 is engaged.

Thereafter, when the engagement control of the third clutch C-3 by the control pressure _{P SL4} linear solenoid valve SL4 is completed, the solenoid valve SR is turned OFF by the control unit. Then, C3 relay valve 12, since the reverse range pressure P _R through the oil passage b7 to the hydraulic oil chamber 12b is inputted, becomes a right-half position, the reverse range pressure P _R is the oil from the B2 relay valve 14 It is input to the input port 12e via the paths k1, k4, k5, and is supplied from the output port 12d to the hydraulic servo 32 of the third clutch C-3 via the oil paths g1, g2, g3. Thus, the third clutch C-3 is engaged state is maintained by the reverse range pressure P _R continues.

By the way, for example, when the linear solenoid valve SL4 breaks down and the control pressure _PSL4 is not output in this reverse gear, the control unit can change any of the input shaft rotational speed change, the output shaft rotational speed change, the vehicle speed, etc. Based on this, it is determined that the third clutch C-3 is not engaged. Then, the control unit turns off the solenoid valve SR as fail control. This state is the same even when, for example, a solenoid, all-off, or failure where all solenoid valves are de-energized due to a short circuit or disconnection. The second brake B-2 B-2 outer oil chamber 32a and the B-2 inner oil chamber 32b, as described above, is supplied with the reverse range pressure P _R, which is engaged state.

When the solenoid valve SR is OFF, C3 relay valve 12, since the reverse range pressure P _R through the oil passage b7 to the hydraulic oil chamber 12b is input, the right-half position. Then, the B2 relay reverse range pressure _{P R} from the valve 14 is input to the input port 12e via the oil paths k1, k4, k5, third clutch C from the output port 12d via the oil passage g1, g2, g3 -3 hydraulic servo 32. Thus, the third clutch C-3, although linear manner pressure-regulated control pressure is not input, is engaged by the reverse range pressure P _R. That is, for example, even when the linear solenoid valve SL4 is in failure (solenoid, all-off, fail), the reverse gear is achieved and a minimum limp home is secured.

  Next, when the quick drain which is the main part of the present invention is changed from the R position (reverse shift position) to the N position (non-travel shift position) (RN), the D position (forward shift position) to the N position. When changed to (non-travel shift position) (D-N), when changed quickly from the R position to the D position via the N position (RD), from the D position to the R position via the N position A case where the change is made quickly (DR) will be described as an example. In this specification, “when quickly changed” refers to a state in which the shift lever (not shown) is stopped at the N position for less than about 0.3 seconds, that is, before the quick drain is finished. This refers to the case where the travel shift position is changed. In the present embodiment, the case of the N position as the non-traveling shift position will be described. Of course, the same applies to the P position.

  First, RN control when the position is changed from the R position to the N position will be described with reference to FIGS. 4 and 6. For example, when the driver selects the N position from the R position by the shift lever and the control unit determines the N position from the R position (S1-1), the solenoid valve SR is turned on by an electronic command from the control unit. And the linear solenoid valve SL4 is turned OFF, and the hydraulic pressure of the hydraulic servo 32 of the third clutch C-3 is drained from the discharge port SL4d of the linear solenoid valve SL4 via the oil passages g3, g1, f1, d3, d1. And the release of the third clutch C-3 is started.

  Subsequently, it is checked (determined) whether the oil temperature is, for example, room temperature (for example, 10 degrees or more) or low temperature (for example, less than 10 degrees) (S1-2), and for example, it is determined that the oil temperature is room temperature. In this case, the solenoid valve SB is turned off by an electronic command from the control unit. Then, the B2 relay valve 14 remains in the left half position due to the urging force of the spring 14s, the spool 20p of the manual valve 20 is in the N range position, and the output port 20d and the drain port EX communicate with each other. The oil is drained from the check ball valve 25 through the oil passages l4, l3, l2, l1, k4, b9, the orifice 46b, the oil passages b8, b3, b1, and the output port 20d (S1-3). As a result, the third clutch C-3 and the second brake B-2 are released, and the automatic transmission 3 becomes neutral (N gear stage) (S1-6).

On the other hand, if it is determined that the oil temperature is low, for example, the solenoid valve SB is turned on by an electronic command from the control unit (S1-4). Then, the B2 relay valve 14 is in the right half position when the signal pressure _PSB is input to the hydraulic oil chamber 14a. For this reason, the hydraulic pressures of the B-2 outer oil chamber 32a and the B-2 inner oil chamber 32b are quickly drained from the drain port EX of the B2 relay valve 14 via the oil passages l4, l3, l1, and k4 (S1- 5) For example, the second brake B-2 is released more quickly than when draining from the check ball valve 25 via the oil passage b9, the orifice 46b, the oil passages b8, b3, b1, and the output port 20d. The Of course, as a result, similarly, the automatic transmission 3 becomes neutral (N gear stage) (S1-6). Thereafter, the solenoid valve SB is turned off after a predetermined time (for example, after 0.3 seconds) when the hydraulic pressures of the B-2 outer oil chamber 32a and the B-2 inner oil chamber 32b should be completely drained.

  Next, the DN control when the position D is changed to the position N will be described with reference to FIGS. 4 and 7. For example, when the driver selects the N position from the D position by the shift lever and the control unit determines the N position from the D position (S2-1), the oil temperature is, for example, normal temperature (for example, 10 degrees or more). It is checked (determined) whether the oil temperature is normal temperature (for example, less than 10 degrees) (S2-2). For example, when it is determined that the oil temperature is normal temperature, the solenoid valve SB is turned off by an electronic command from the control unit To maintain. Then, the C1 relay valve 15 remains in the left half position by the urging force of the spring 14s, and when the linear solenoid valve SL1 is turned off, the hydraulic pressure of the first clutch C-1 via the oil passages c6, c4, and c3. The hydraulic pressure of the servo 31 is drained from the discharge port SL1d of the linear solenoid valve SL1 (S2-3). As a result, the first clutch C-1 is released and the automatic transmission 3 becomes neutral (N gear stage) (S2-6).

On the other hand, when it is determined that the oil temperature is low, for example, the solenoid valve SB is turned on by an electronic command from the control unit (S2-4). Then, the C1 relay valve 15 is in the right half position when the signal pressure _PSB is input to the hydraulic oil chamber 15a. For this reason, the output port 15c and the connection port 15d of the C1 relay valve 15 communicate with each other, and the spool 20p of the manual valve 20 enters the N range position so that the output ports 20b and 20c communicate with the drain port EX. Therefore, the hydraulic pressure of the hydraulic servo 31 of the first clutch C-1 is quick drained from the check ball valve 26 through the oil passages c6, c4, a4, a3, a1, and for example, the oil passages c6, c4, c3 and linear The first clutch C-1 is quickly released as compared with the case of draining from the check ball valve 27 via the solenoid valve SL1. Of course, as a result, similarly, the automatic transmission 3 becomes neutral (N gear stage) (S2-6). Thereafter, the solenoid valve SB is turned off after a predetermined time (for example, after 0.3 seconds) when the hydraulic pressure of the hydraulic servo 31 of the first clutch C-1 should be completely drained.

  Next, a case where the position is quickly changed from the R position to the D position via the N position (RD) will be described with reference to FIGS. 4 and 8. For example, when the driver quickly operates from the R position to the D position through the N position by the shift lever, first, the N position is detected by the control unit, and thus RN control is performed. Since steps S1-1 to S1-6 in FIG. 8 are the same as those described above, the description thereof is omitted.

Here, for example, when the oil temperature is determined to be low in the above-described RN control and the solenoid valve SB is turned on and quick drain is performed (S1-4, S1-5), the solenoid valve SB Even when the D position is determined before turning OFF, it is necessary to immediately engage the first clutch C-1. However, for example, C1 position of quick draining relay valve 15 by the signal pressure _{P SB} of the solenoid valves SB, i.e. to the right half position, since the output port 15c and a connection port 15d are communicated, the input port 20a of the manual valve 20 the line pressure _{P L} is supplied from being supplied to the first hydraulic servo 31 of the clutch C-1 via the oil passage a1, a3, a4, c4, c6 as the forward range pressure _{P D} to (S3-a) . Therefore, although the first clutch C-1 is engaged in the first forward speed is achieved, engaged abruptly engaged by the line pressure P _L, it occurs engagement shock, i.e. poor shift feel (S3-B).

Therefore, in the hydraulic control apparatus 10, when the control unit determines the ND control, first, the solenoid valve SR is turned on to connect the input port 12f and the output port 12g of the C3 relay valve 12, and the manual valve 20 output port 20b of the oil passage to the forward range pressure _{P D} from 20c a1, a2, a5, a6 , a7 signal pressure P to the hydraulic oil chamber 15e of the (second forward range pressure oil channel) C1 relay valve 15 via the _An input is made to _{face SB} . Thus, C1 relay valve 15, regardless of the input state of the signal pressure _{P SB,} becomes left-half position, the oil passage c1, c3, c4, c6 (forward engagement oil passage, the control pressure supply passage) communicates the Te, and supplies to the hydraulic servo 31 of the control pressure _{P SL1} first clutch C-1 of the linear solenoid valve SL1 as described above (S3-2). In other words, since the engagement pressure P _C1 supplied to the hydraulic servo 31 of the first clutch C1 is the first forward speed is achieved is smoothly controlled by the linear solenoid valve SL1, the better as the shift feel (S3- 3).

Incidentally, the check ball (delay means) 42 in the oil passage a4 are disposed, is delaying that forward range pressure P _D from the oil path a4 to the oil path c4 supplied. Therefore, before the forward range pressure _{P D} to the first hydraulic servo 31 of the clutch C-1 via the oil passage c4 from the oil path a4 is supplied, through the oil passage a1, a2, a5, a6, a7 forward range pressure _{P D} to the hydraulic oil chamber 15e of the C1 relay valve 15 is input. Thus, it is supplied with the forward range pressure P _D to the first hydraulic servo 31 of the clutch C-1, preventing the abrupt engagement as described above occurs is achieved.

Further, after the first forward speed is achieved in this way and the quick drain of the second brake B-2 is completed, the solenoid valve SB and the solenoid valve SR are turned off. The C3 relay valve 12, the oil passage a1, a3, a5, a8, a9 and the forward range pressure _{P D} to the hydraulic oil chamber 12a via the (third forward range pressure oil channel) is input, the solenoid valve SR There is turned OFF, the signal pressure P _SR is not input to the hydraulic oil chamber 12j, it is switched from the left-half position in the right half position. Then, the oil passage a6 and the oil passage a7 (second forward range pressure oil passage) are blocked by the C3 relay valve 12, and the signal pressure _PSB is not input to the hydraulic oil chamber 15a of the C1 relay valve 15. , the forward range pressure P _D to the hydraulic oil chamber 15e is not input by the biasing force of the spring 15s, the C1 relay valve 15 is maintained at the left half position. Thus, C1 is to block the forward range pressure _{P D} for the hydraulic oil chamber 15e of the relay valve 15, the next D-N control, upon turning ON the solenoid valve SB, the signal pressure P to the hydraulic oil chamber 15a _SB can be input to switch to the right half position, that is, quick drain in the next DN control can be enabled.

  Next, a case where the position is quickly changed from the D position to the R position via the N position (D−R) will be described with reference to FIGS. 4 and 9. For example, when the driver quickly operates the shift lever from the D position to the R position through the N position, first, the N position is detected by the control unit, and thus DN control is performed. Note that steps S2-1 to S2-6 in FIG. 9 are the same as those described above, and a description thereof will be omitted.

Here, for example, when the oil temperature is determined to be low in the above-described DN control and the solenoid valve SB is turned on and quick drain is performed (S2-4, S2-5), the solenoid valve SB Even when the R position is determined before turning OFF, it is necessary to immediately engage the second brake B-2. However, for example, the B2 relay valve 14 is located in the quick draining by the signal pressure P _SB of the solenoid valves SB, i.e. to the right half position, the input port 14d and the output port 14e are blocked, and the oil passage b9 and the oil passage k1 The reverse engagement oil passage and the first reverse range pressure oil passage are blocked.

With this state, the reverse range pressure _{P R} is fed to the input port 11c of the C3B2 relay valve 11 via the oil passage b1, b2 (S4-A) , the rear proceeds range pressure _{P R} C3B2 output of relay valve 11 The oil is supplied from the port 11e to the input port 13c of the B2 cutoff valve 13 through the oil passage e1 (S4-B), and further from the output port 13d of the B2 cutoff valve 13 to the input of the B2 relay valve 14 through the oil passage e2. Is supplied to the port 14c (S4-C), and is supplied from the output port 14b of the B2 relay valve 14 to the B-2 outer oil chamber 32a and the B-2 inner oil chamber 32b through the oil passages j1, l1, l2, l3, and l4. the second brake B-2 engaged by supplying (S4-D), then the third click the control pressure _{P SL4} linear solenoid valve SL4 as described above The pitch C-3 engages becomes (S4-E) it. Therefore, the time until the reverse gear is achieved is delayed, and a time lag occurs until the reverse gear is achieved after changing to the R range.

Therefore, in the hydraulic control apparatus 10, when the control unit determines the N-R control, first, the solenoid valve SR is turned on, the input port 12h and the output port 12i of the C3 relay valve 12 are communicated, and the manual valve 20 the reverse range pressure _{P R} from the output port 20d of the oil passage b1, b3, b4, b5, b6 to the hydraulic oil chamber 14f of the B2 (second reverse range pressure oil passage) through the relay valve 14 to the signal pressure _{P SB} Input oppositely. Also, previously supplied to the reverse range pressure _{P R} oil passage b1, b3, b8, directly through b9 (direct) the B2 input port 14d of the relay valve 14 (S4-2). Thus, B2 relay valve 14, regardless of the input state of the signal pressure _{P SB,} becomes left-half position, the oil passage b1, b3, b8, b9, k1, k2, k3, k4, l1, l2, l3, l4 (reverse engagement oil passage, the first reverse range pressure oil passage) and made to communicate with, and supplies the reverse range pressure P _R to the B-2 outer oil chamber 32a and the B-2 inner oil chamber 32b as described above, The second brake B-2 is engaged (S4-3). Thereafter, engaging the third clutch C-3 by the control pressure _{P SL4} linear solenoid valve SL4 as described above (S4-4). As a result, the reverse gear is quickly achieved without causing the time lag as described above.

Further, after the reverse gear is achieved in this way and the quick drain of the first clutch C-1 is completed, the solenoid valve SB and the solenoid valve SR are turned off. C3 The relay valve 12, b1, b3, b4, b7 and the reverse range by pressure _{P R} is input (third reverse range pressure oil passage) via the hydraulic oil chamber 12b, the solenoid valve SR is OFF When the hydraulic oil chamber 12j to the signal pressure P _SR is not input, it is switched from the left-half position in the right half position. Then, the oil passage b5 and the oil passage b6 (second reverse range pressure oil passage) are blocked by the C3 relay valve 12, and the signal pressure _PSB is not input to the hydraulic oil chamber 14a of the B2 relay valve 14. , the reverse range pressure P _R is not input to the hydraulic oil chamber 14f, by the urging force of the spring 14s, the B2 relay valve 14 is maintained in the left half position. Thus, B2 is blocking the reverse range pressure _{P R} for the hydraulic oil chamber 14f of the relay valve 14, in the next R-N control, upon turning ON the solenoid valve SB, the signal pressure P to the hydraulic oil chamber 14a _SB can be input to switch to the right half position, that is, quick drain in the next RN control can be enabled.

As described above, according to the hydraulic control device 10 for an automatic transmission according to the present invention, when the reverse shift position is changed to the non-travel shift position, and when the forward shift position is changed to the non-travel shift position, by changing the output state of the signal pressure _{P SB} of the solenoid valves SB, B2 relay discharge position the valve 14 and the C1 relay valve 15 switched to (4 in the right half position), the hydraulic servo 33 of the second brake B2 When the reverse shift position is changed to the non-travel shift position, and the forward shift position is changed to the non-travel shift position, the quick drain of the hydraulic pressure of the first servo and the hydraulic servo 31 of the first clutch C-1 is performed. The solenoid valve can be used while quick drain can be performed on both sides. Only one renoid valve SB is sufficient, cost reduction can be achieved, and simultaneous engagement due to, for example, a shift in the control timing of the two solenoid valves does not occur, and shift shock can be prevented.

Further, in the case at least a low oil temperature, since the quick draining by changing the output state of the signal pressure P _SB of the solenoid valves SB, drain is delayed due to the viscosity of oil is high, the second brake B- 2 and the first clutch C-1 can be prevented from being left unengaged.

Further, since the oil passage c1, c3, c4, c6 is a control pressure _{P SL1} of the linear solenoid valves SL1 to the hydraulic servo 31 of the first clutch C1 is oil passage for supplying the engagement pressure _{P C1,} linear solenoid When the hydraulic pressure of the hydraulic servo 31 of the first clutch C-1 is drained by the pressure regulating operation of the valve SL1, the drain may be delayed particularly when the oil temperature is low, but the quick drain is performed by switching the C1 relay valve 15. Therefore, the remaining engagement can be prevented.

Further, the C1 relay valve 15 communicates the oil passages c4 and c6 to the hydraulic servo 31 of the first clutch C-1 and the output ports 20b and 20c of the manual valve 20 at the right half position as the discharge position. because it is connected to the oil path a1, a3, a4, the output port 20b of the manual valve 20, through 20c, hydraulic pressure of the quick draining of the first hydraulic servo 31 of the clutch C-1 with the drain of the forward range pressure _{P D} It can be performed.

Moreover, C1 relay valve 15, oil path for supplying forward range pressure P _D so as to urge the left half position side which is the engaged position when it is changed to the forward shift position from the non-travel shift position a1, a2 , A5, a6, a7, for example, when the driver quickly changes from the reverse shift position to the forward shift position, the signal pressure PSB of the solenoid valve _SB is output and the B2 relay valve 14 is discharged. switching a is in the right half position location, and the C1 relay valve 15, irrespective of the signal pressure P _SB of the solenoid valves SB, can be switched to the left half position by the forward range pressure P _D. Thus, while performing hydraulic quick drain of the second brake B-2 of the hydraulic servo 33, the first clutch C1 by supplying the engagement pressure _{P C1} to the hydraulic servo 31 of the first clutch C1 Engagement can be performed.

Furthermore, it interposed in an oil passage a1, a3, a4, oil passages a1, a2, a5, a6, a7 from than the forward range pressure _{P D} supplied to the C1 relay valve 15, the oil passage a1, a3, a4 from C1 is provided with the check ball 42 for delaying the forward range pressure P _D supplied to the relay valve 15, the oil passage a1, a3, a4 forward range pressure P _D supplied from the first clutch C-1 of the hydraulic servo before being supplied to 31, it is possible to switch the oil passages a1, a2, a5, a6, the forward range pressure _P C1 relay valve 15 by _D from a7 to the left half position. Thus, for example, the forward range pressure P _D is not to be supplied to the oil passage a1, a3, a4 first hydraulic servo 31 of the clutch C-1 in the form of flow back for performing quick draining and original oil road c1, c3, c4, c6 and can supply the engagement pressure _{P C1} to the hydraulic servo 31 of the first clutch C1 via, that the forward range pressure _{P D} is sharply first clutch C1 It is possible to prevent a sudden engagement of the first clutch C-1 from being supplied to the hydraulic servo 31.

Further, connected to the oil path a1, a2, a5, a6, a7 oil passage for supplying the forward range pressure _{P D} with intervening a1, a3, a5, a8, a9, the oil passage in the non-travel shift position a1 , it is switched to a2, a5, a6, a7 left half position is communicating position to communicate the inputs oil passages a1, a3, a5, a8, the forward range pressure _{P D} from a9 during forward shift position, in the blocking position for blocking the oil passages a1, a2, a5, a6, a7 by the urging of the forward range pressure _{P D} from the oil path a1, a3, a5, a8, a9 after first engagement of the clutch C-1 is provided with the C3 relay valve 12 is switched to a right-half position, when it is changed to the forward shift position from the non-driving shift position, the oil passage a1, a2, a5, a6, the forward range pressure P _D from the a7 C1 relay bar Is supplied to the lube 15 can be switched on regardless left half position the C1 relay valve 15 to the signal pressure _{P SB} of the solenoid valves SB, after engagement of the first clutch C1, the oil passage a1, a2, a5, a6, since a7 is interrupted, when changing from the forward shift position to another shift position, it can be switched to the right half position C1 relay valve 15 by the signal pressure P _SB of the solenoid valves SB, Quick A drain can be performed.

On the other hand, the oil passage b1, b3, b8, b9, k1, k2, k3, k4, l1, l2, l3, l4 , the engagement pressure P the reverse range pressure _{P R} to the second hydraulic servo 33 of the brake B-2 _{Since the} oil passage is supplied as _B2 , there is a risk that the drain will be delayed particularly when the oil temperature is low, but the quick drain can be performed by switching the B2 relay valve 14, so that the remaining engagement can be prevented. Can do.

Also, B2 relay valve 14, oil path for supplying reverse range pressure P _R to bias the left half position side which is the engagement position in the non-travel shift position is changed to the reverse shift position b1, b3 , B4, b5, and b6, for example, when the driver quickly changes from the forward shift position to the reverse shift position, the signal pressure PSB of the solenoid valve _SB is output and the C1 relay valve 15 is moved to the right. It switched to the half position, and the B2 relay valve 14, irrespective of the signal pressure P _SB of the solenoid valves SB, can be switched to the left half position by the reverse range pressure P _R. Thus, while performing quick drain of the hydraulic servo 31 of the first clutch C-1, the engagement pressure P _B2 is supplied to the hydraulic servo 33 of the second brake B-2, and the second brake B-2 Engagement can be performed.

Further, the oil passage b1, b3, b4, b5, b6 oil passage for supplying the reverse range pressure _{P R} with interposed b1, b3, b4, is connected to b7, the oil passage b1, b3 during non-travel shift position , b4, b5, b6 switched to the left half position is communicating position to communicate the, type the oil passage b1, b3, b4, the reverse range pressure _{P R} from b7 during reverse shift position, the second brake B oil passage b1 after engagement of -2, b3, b4, the oil passage by the biasing of the reverse range pressure _{P R} from b7 b1, b3, b4, b5 , b6 switched to the right half position is a blocking position for blocking the since C3 and a relay valve 12 which is, when the non-travel shift position is changed to the reverse shift position, the supply oil passage b1, b3, b4, b5, b6 from the reverse range pressure _{P R} to the B2 relay valve 14 do it The B2 relay valve 14 can be switched on regardless left half position signal pressure _{P SB} of the solenoid valves SB, after engagement of the second brake B2 is an oil passage b1, b3, b4, b5, b6 Since it is cut off, when the reverse shift position is changed to another shift position, the B2 relay valve 14 can be switched to the right half position by the signal pressure P _SB of the solenoid valve SB, and quick drain can be performed. .

The C3 relay valve 12 is interposed between the linear solenoid valve SL4, the hydraulic servo 32 of the third clutch C-3, and the output port 20d of the manual valve 20. The C3 relay valve 12 is connected to the linear solenoid valve SL4 when the left half position is reached. The hydraulic servo 32 of the third clutch C-3 is communicated, and the output port 20d of the manual valve 20 and the hydraulic servo 32 of the third clutch C-3 are communicated when the right half position is reached. upon inputting the signal pressure P _SR, irrespective of the reverse range pressure P _R from the oil passage b7, it is switched to the left half position, when the signal pressure P _SR of the solenoid valve SR is non-input, from the oil passage b7 reverse range by pressure P _R, it is switched to the right half position, the oil even in the event of a failure of the linear solenoid valve SL4 to the reverse range pressure P _R third clutch C-3 of Since it consists of a valve for security to be supplied to the servo 32, communication / blocking of the oil passages a1, a2, a5, a6, a7 and the oil passages b1, b3, b4, b5, b6 without providing another switching valve Therefore, it is possible to reduce the number by sharing the switching valve, and it is possible to reduce the size and cost.

  Furthermore, the hydraulic control device 10 for an automatic transmission according to the present invention can be applied to the hybrid drive device 1. Further, in the hybrid drive device 1, for example, when the non-travel shift position is switched to the forward shift position or the reverse shift position, the rising of the torque output of the first and second motors M <b> 1 and M <b> 2 occurs in the internal combustion engine 4. In contrast, when the first clutch C-1 and the second brake B-2 are left unengaged, a shift shock occurs. However, according to the present invention, the hydraulic servo 31 and the second clutch of the first clutch C-1 are generated. Since a quick drain for the hydraulic servo 33 of the brake B-2 is enabled, a shift shock can be prevented.

  In the above-described embodiment, the automatic transmission hydraulic control device 10 is applied to the hybrid drive device 1. However, of course, the present invention is also applied to an automatic transmission using only an internal combustion engine as a drive source. The invention can be applied. Further, the automatic transmission that achieves the fourth forward speed and the first reverse speed has been described. However, the present invention is not limited to this, and a friction engagement element that engages when moving forward and a friction engagement element that engages when moving backward Any automatic transmission may be used as long as it is provided.

  In the present embodiment, the second brake B-2 is used as the reverse friction engagement element and the first clutch C-1 is used as the forward friction engagement element. However, the present invention is not limited to this. The present invention can be applied to any device provided with a reverse friction engagement element and a forward friction engagement element.

The skeleton figure which shows the hybrid drive device which concerns on this invention. Automatic transmission engagement table. The speed diagram of an automatic transmission. BRIEF DESCRIPTION OF THE DRAWINGS Schematic which shows the hydraulic control apparatus of the automatic transmission which concerns on this invention. A partially omitted cross-sectional view showing a check ball valve. The flowchart which shows the operation | movement at the time of RN. The flowchart which shows the operation | movement at the time of DN. The flowchart which shows the operation | movement at the time of RD. The flowchart which shows the operation | movement at the time of DR.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Hybrid drive device 2 Hybrid drive part 2b Drive shaft 3 Automatic transmission 4 Internal combustion engine 10 Hydraulic control device 12 of automatic transmission Third switching valve, security valve (C3 relay valve)
14 First switching valve (B2 relay valve)
15 Second switching valve (C1 relay valve)
20 Range pressure switching valve (manual valve)
20b, 20c Forward range pressure output port 20d Reverse range pressure output port 31 Hydraulic servo 33 for forward friction engagement element (first clutch) Hydraulic servo 42 for backward friction engagement element (second brake) Delay means (check ball) )
PR ₀ power distribution mechanism (power distribution planetary gear)
M1 first motor M2 second motor C-1 forward friction engagement element (first clutch)
C-3 Reverse clutch (third clutch)
B-2 Reverse friction engagement element, reverse brake (second brake)
P, N Non-traveling shift position (P position, N position)
D Forward shift position (D position)
R Reverse shift position (R position)
SB 1st signal solenoid valve (solenoid valve)
SR 2nd signal solenoid valve (solenoid valve)
SL1 First pressure regulating solenoid valve (Linear solenoid valve)
SL4 Second pressure regulating solenoid valve (Linear solenoid valve)
P _D Forward range pressure P _R Reverse range pressure P _SB signal pressure P _SR signal pressure P _SL1 control pressure P _SL4 control pressure P _C1 engagement pressure P _B2 engagement pressure c1, c3, c4, c6 Forward engagement oil path, control Pressure supply oil passage b1, b3, b8, b9, k1, k2, k3, k4, l1, l2, l3, l4 Reverse engagement oil passage, first reverse range pressure oil passage a1, a3, a4 First forward range pressure Oil path a1, a2, a5, a6, a7 Second forward range pressure oil path a1, a3, a5, a8, a9 Third forward range pressure oil path b1, b3, b4, b5, b6 Second reverse range pressure oil path b1, b3, b4, b7 Third reverse range pressure oil passage

Claims (12)

A forward friction engagement element that is engaged when the non-travel shift position is changed to the forward shift position and is released when the forward shift position is changed to the non-travel shift position; And a reverse friction engagement element that is engaged when the reverse shift position is changed and is released when the reverse shift position is changed to the non-travel shift position. In
A first signal solenoid valve capable of outputting a signal pressure;
Based on the output state of the signal pressure of the first signal solenoid valve, the reverse engagement oil passage is communicated with the reverse engagement oil passage that supplies engagement pressure to the hydraulic servo of the reverse friction engagement element. A first switching valve that is switched to an engagement position and a discharge position that can be drained earlier than to drain using the reverse engagement oil passage;
Based on the output state of the signal pressure of the first signal solenoid valve, the forward engagement oil passage is communicated with the forward engagement oil passage for supplying an engagement pressure to the hydraulic servo of the forward friction engagement element. A second switching valve that is switched to an engagement position and a discharge position that can be drained earlier than to drain using the forward engagement oil passage;
When the reverse shift position is changed to the non-travel shift position and when the forward shift position is changed to the non-travel shift position, the output state of the signal pressure of the first signal solenoid valve is changed, The hydraulic servo hydraulic pressure of the reverse friction engagement element and the hydraulic servo hydraulic pressure of the forward friction engagement element are configured to be able to perform a quick drain.
A hydraulic control device for an automatic transmission. At least at the time of low oil temperature, the quick drain is performed by changing the output state of the signal pressure of the first signal solenoid valve,
The hydraulic control device for an automatic transmission according to claim 1. Comprising a first pressure regulating solenoid valve capable of supplying a control pressure regulated to the hydraulic servo of the forward friction engagement element;
The forward engagement oil passage is a control pressure supply oil passage that supplies the control pressure of the first pressure regulating solenoid valve as the engagement pressure to the hydraulic servo of the forward friction engagement element.
The hydraulic control device for an automatic transmission according to claim 1 or 2, A forward range pressure is output at the forward shift position, and a forward range pressure output port for draining the forward range pressure at other shift positions, and a reverse range pressure is output at the reverse shift position, And a reverse range pressure output port for draining the reverse range pressure at other shift positions, and a range pressure switching valve having a reverse range pressure output port,
The second switching valve has a first forward range pressure oil passage that communicates the forward engagement oil passage to the hydraulic servo of the forward friction engagement element and the forward range pressure output port at the discharge position. Connected to the
The hydraulic control device for an automatic transmission according to any one of claims 1 to 3. The first and second switching valves are biased toward the discharge position when the signal pressure of the first signal solenoid valve is input,
The second switching valve is connected to a second forward range pressure oil passage that supplies the forward range pressure so as to be biased toward the engagement position when the non-travel shift position is changed to the forward shift position. Become,
The hydraulic control device for an automatic transmission according to claim 4. The second switching valve from the first forward range pressure oil passage is more than the forward range pressure interposed in the first forward range pressure oil passage and supplied from the second forward range pressure oil passage to the second switching valve. Provided with delay means for delaying the forward range pressure supplied to the
The hydraulic control device for an automatic transmission according to claim 5. Communication that is interposed in the second forward range pressure oil passage and is connected to a third forward range pressure oil passage that supplies the forward range pressure, and communicates with the second forward range pressure oil passage in the non-travel shift position. The forward range pressure from the third forward range pressure oil passage is input at the forward shift position, and after the forward friction engagement element is engaged, the forward travel range pressure from the third forward range pressure oil passage is input. A third switching valve that is switched to a blocking position that blocks the second forward range pressure oil passage by energizing the forward range pressure;
The hydraulic control device for an automatic transmission according to claim 5 or 6. The reverse engagement oil passage is a first reverse range pressure oil passage that supplies the reverse range pressure as the engagement pressure to the hydraulic servo of the reverse friction engagement element.
The hydraulic control device for an automatic transmission according to any one of claims 5 to 7. The first switching valve is connected to a second reverse range pressure oil passage that supplies the reverse range pressure so as to be biased toward the engagement position when the non-travel shift position is changed to the reverse shift position. Become,
The hydraulic control apparatus for an automatic transmission according to claim 8. Communication that is interposed in the second reverse range pressure oil passage and is connected to a third reverse range pressure oil passage that supplies the reverse range pressure, and communicates with the second reverse range pressure oil passage in the non-travel shift position. When the reverse shift position, the reverse range pressure from the third reverse range pressure oil path is input, and after the reverse friction engagement element is engaged, the reverse range pressure oil path from the third reverse range pressure oil path is input. A third switching valve that is switched to a shut-off position that shuts off the second reverse range pressure oil passage by energizing the reverse range pressure;
The hydraulic control device for an automatic transmission according to claim 9. The reverse friction engagement element comprises a reverse brake,
The automatic transmission includes a reverse clutch that is engaged with the reverse brake at the reverse shift position,
A second signal solenoid valve that outputs a signal pressure when the non-travel shift position is changed to the reverse shift position;
A second pressure regulating solenoid valve capable of supplying a control pressure regulated to the hydraulic servo of the reverse clutch,
The third switching valve is interposed between the second pressure regulating solenoid valve, a hydraulic servo of the reverse clutch, and a reverse range pressure output port of the range pressure switching valve, and the second switching valve is located at the communication position. Communicating the pressure regulating solenoid valve and the hydraulic servo of the reverse clutch, and communicating the reverse range pressure output port of the range pressure switching valve and the hydraulic servo of the reverse clutch at the shut-off position; When the signal pressure of the second signal solenoid valve is input, the signal is switched to the communication position regardless of the reverse range pressure from the third reverse range pressure oil passage, and the signal pressure of the second signal solenoid valve is not At the time of input, the reverse range pressure from the third reverse range pressure oil passage is switched to the shut-off position by the reverse range pressure, and the reverse range pressure is changed to the reverse clutch even when the second pressure regulating solenoid valve is in failure. Hydraulic servo Consisting of security for the valve supply,
The hydraulic control device for an automatic transmission according to claim 10. A hybrid drive unit configured to distribute the drive force from the internal combustion engine to the first motor and the drive shaft by a power distribution mechanism and to apply the drive force of the second motor to the drive shaft;
The automatic transmission capable of shifting the rotation of the drive shaft of the hybrid drive unit;
A hydraulic control device for an automatic transmission according to any one of claims 1 to 11,
A hybrid drive device characterized by that.

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